DE2121307A1 - Braking device - Google Patents

Description

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Hans Gfeller Langeηthai (Switzerland)

Braking device

The invention relates to a blowing device for braking parts moving relative to one another, with one pressurized by a medium when the brake is released and for braking pressure-relieved cylinders.

Known braking devices of this type, which work hydraulically and for braking, for example, a vehicle serve, have the disadvantage that a certain delay that can be achieved by them in the loading of the vehicle, the friction factor of the braking elements and, if it is z. B. is a vehicle on a mountain railway, "is dependent on the downhill force of the vehicle, the specific deceleration For example, a value that is still permissible to guarantee that the vehicle occupants will not be able to sneeze off represents, but if exceeded, the occupants fall and could be injured. In particular In the case of mountain railways, the routes between individual stations and in the area of the stations are different. Slope, so that the different downhill drifts

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visibly different from reaching the specific delay affects, whereby the possible different vehicle load by occupants is a further influencing factor represents.

The invention is based on the object of, for example, a certain deceleration with a braking device of a vehicle regardless of its payload, downhill drift and the friction factor of the braking elements. The braking device of the type mentioned at the outset is therefore characterized according to the invention in that, for the deceleration-controlled Braking the cylinder via a non-return valve with a pressure accumulator to accommodate part of the medium escaping from the cylinder and is also connected via a throttle point to a deceleration controller which one with a relative movement sensor in driving connection stationary centrifugal mass and a leading of the centrifugal mass compared to the relative movement pick-up up to a predetermined one Delay value counteracting force member and also a shut-off element cooperating with the flywheel for the sailor under increasing pressure reduction flowing through until the predetermined delay value is reached Having medium, after the closing of the shut-off element caused by the flywheel, the pressure of the Medium remains constant for further braking. The Eelative— The movement detector of the deceleration controller can preferably have a shaft that moves at one of the relative speeds the angular velocity corresponding to the relative moving parts rotates, and this shaft can expediently be rotatably mounted coaxially in a cylindrical housing at both ends and within the housing itself carry rotating flywheel, which is useful by means of a are arranged between the shaft and the flywheel carrier with the shaft in driving connection and against the

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Effect of the force link between the shaft and the flywheel, which is preferably a spiral spring, can be moved relative to the shaft, inter alia, a limited angle of rotation can. The shut-off device that works together with the flywheel can be a rotary valve, preferably from a rotatable on the shaft, ring-shaped and old radial bores coupled to the flywheel and from one «preferably one coaxial and several old this related radial bores having shaft section can exist whose radial bores for the passage of the medium when the shut-off device is open the radial bores are aligned with the generally annular valve body, in which case this valve body is then expediently in front of the flywheel relative to the shaft against the force of the spiral spring can close the bores in the shaft. The spiral spring that acts between the shaft and the flywheel is suitably preloaded, and by the size of the spring preload the size of the delay can be determined.

Further features, details and advantages of the invention emerge from the claims, the description and the drawings, in which an embodiment of the subject matter of the invention is shown purely as an example. Show it:

Pig. 1 the hydraulic scheme of the area facility for a rail-bound vehicle;

fig. 2 shows the deceleration controller belonging to the breather device, generally in a longitudinal section;

fig. 3, 4 and 5 different cross-sections through the deceleration regulator along the line AA, the line BB and the line C - G in FIG. 2;

fig. 6 shows a modified embodiment of the delay regulator, generally in longitudinal section;

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Pig. 7, 8 and 9 different cross-sections through the delay controller along the line D-D, the line E-E and the line F-F in FIG. 6.

In the embodiment described below it is about a spring-loaded brake for a funicular. The braking device can, however, basically be used for all types of vehicles and drives for aerial and funicular railways Find application, be it in the pore of a Pederspeieher brake or a direct acting hydraulic brake.

Β Pig recovered from the blower. 1 promotes a motor pump 1 pressurized oil in a spring-loaded cylinder 7, several of which are present on a vehicle. The pressure oil arrives first of all via a check valve 2, and a preload valve 5 ensures that a brake valve 6 is first installed on the spring-loaded cylinder is pressurized and thereby closed. The pressure oil can then be fed in via the preload valve 5 in reach the spring-loaded cylinder 7, the brake being released by the pressurized cylinder by the Spring force is canceled. At the same time, an accumulator 4 is charged in order to avoid possible leakage losses via a non-return throttle 3 cover up. The braking device is thus ready for operation.

A release valve 8 to which the same oil pressure is applied is actuated for braking. This can be done by hand take place or by an overspeed switch, or by each hot brake lever in the vehicle or also automatically in the event of a rope break if the braking device is used on a cable car. When actuated of the trigger valve 8, the pressure is relieved from the brake valve 6, since the pressurized oil flows back to the pump via the trigger valve 8 can. Each of the existing spring-loaded cylinders 7 is assigned a memory 9, in which the pressure oil is now at

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open brake valve 6 can escape via a check valve 10 under pressure reduction. In each memory 9 is located a pre-tensioned gas that counteracts the pressure of the oil, and the gas pre-tension determines the size the initial braking force and thus the initial deceleration of the vehicle by the oil pressure counteracting the spring force in the cylinder 7 can only be reduced to the point of pressure equalization with the gas in the memory 9. In the memory 9 to Pump returning line, a throttle 11 is provided, which is used to maintain the pressure during this initial Braking process ensures. '

Of which the brake valve 6 with the memory 9 connecting Line branches off another line through which the Drufcöl via a throttle 12 to a deceleration controller 13 which regulates the pressure oil up to a predetermined deceleration value flows through, whereby the pressure in the spring-loaded cylinder is further reduced and thus that associated with the further braking Deceleration of the vehicle up to the predetermined value increases.

In the embodiment of a rail-bound vehicle shown here, a running wheel H of the vehicle forms which rolls on the rail 15 and drives a shaft 17 via a pair of gears 16, the relative movement sensor of the delay controller 13, which interrupts the reduction of the oil pressure when a predetermined delay is reached, so that the braking force no longer increases.

In the case of the delay controller shown in more detail in FIGS 13, the shaft 17 is rotatably mounted coaxially in a cylindrical housing 18 at both ends. On this wave is a circular in cross section centrifugal mass 19 relative to the shaft by an angle of rotation of about 15 ° to 20 ° rotatably mounted and is by means of a driver 20 in

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Driving connection with the shaft. The twist of the A spiral spring 21 counteracts the flywheel opposite the shaft, one end of which by means of a threaded bolt 22 on the flywheel 19 and at its other end is fixed in a non-rotatable disc 23 on the shaft and, due to its bias, the driver and the flywheel are in contact holds. As can be seen from FIG. 2, the flywheel 19 consists of two screwed together for structural reasons Share.

One end of the shaft 17 has a blind hole 24 running on the central axis, the four of which are at 90 ° to one another offset radial bores 25 in the shaft in communication, and on this shaft section is an annular Valve body 26 with two diametrically opposed radial bores 27 rotatably arranged on the shaft so that that the radial bores in the shaft and in the valve body can be aligned with one another. The valve body 26 is, as from Pig. 5 can be seen, coupled to the flywheel 19 by means of a pin 28. The shaft and the valve body form accordingly together a rotary valve, and as long as the shaft and the flywheel rotate at the same speed, flows the pressure oil entering through a bore 29 in the housing (Pig. 2) through the bores in the shaft and in the valve body through and through a line 30, which is connected to the housing, out of this again. This can the pressure of the oil in the spring-loaded cylinder of the braking device continues to decrease. Through the associated increasing delay occurs between the flywheel 19 and the shaft 17 an increasing, against the Coil spring 21 acting on a force which causes a rotation of the valve body 26 coupled to the flywheel the shaft 17 brings about, whereby the rotary valve is closed. This interrupts the further reduction in the oil pressure, and the further braking takes place with the at this point in time

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prevailing pressure ia spring-loaded cylinder. The bias the spiral spring 21 is the size of the delay.

Since the valve body 26 is closed »rotary valve the shaft has 17 tier bores evenly distributed over the surface, even if only two τοη these bits coaa the bores ia valve body to * align. In the embodiment of the braking device described here, which at a «vehicle for use koaat, animal spring-loaded cylinders are gated, each of the breasaittel in fora a pair of pliers pressed against the rail on both sides, and at the height of each of these cylinders is a storage rather planned. In general, the facility has a ™

Delay regulator, and also the Puape and the other aggregates are only available once.

A modified embodiment of a delay controller is shown in FIGS. 6 to 9 * With this embodiment of the delay controller, the goal is pursued to be able to constantly check whether the deceleration controller is the most important link within the Breas facility Task performed correctly, and if malfunctions of any kind occur, this should be able to be indicated, to which a Purpose of a display device Toa actual deceleration controller removed, for example in general the driver's cab of the vehicle ges should be provided. If in the case of Breasen the vehicle is decelerating and there is a relative movement between the flywheel and the shaft, this relative movement is an indication ensure that the delay controller works correctly and that the shut-off device for the flow of the oil through the controller is involved Reaching a specified delay is closed. at However, it is a shut-off device, which in the case of the delay regulator according to FIGS. 2 to 5 is formed as a rotary valve kaua aöglioh, the movement of the rotary valve from the deceleration

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to the outside to be used as a display to serve. The rotary movement should therefore be converted into an axial movement for the purpose of an outwardly forwarding display implemented, which is realized in the delay controller described below.

The delay controller shown in FIGS otherwise has the same puncture as the one previously described Delay controller. In the case of the deceleration controller designated here as a whole by 113, a shaft 117 is coaxial in FIG a cylindrical housing 118 rotatably mounted at both ends. On this shaft 117 a flywheel 119 is relatively opposite the shaft rotatably through an angle of rotation of about 15 ° to 20 ° and is by means of a driver 120 in close connection with the shaft 117. A spiral spring acts on the rotation of the flywheel relative to the shaft 121 opposite, which at one end by means of a threaded bolt 122 (Fig. 7) on the flywheel 119 and with its other end is fixed in a non-rotatable on the shaft disc 123 and by their bias drivers and Keeps the flywheel in contact.

Up to a predetermined delay value, which is as a result of the pretensioning of the spiral spring, the medium, for example the pressure oil, should act as the deceleration regulator flow through, and then should when the delay value is exceeded a shut-off device is closed by the inertia of the flywheel in relation to the shaft, whereby the flow of the pressure oil from the brake cylinder is interrupted and the braking force no longer increases. That The shut-off device activated when the centrifugal mass is in front of the shaft is a piston valve in this deceleration regulator, of a piston 125 and which is axially movable in a coaxial bore 124 in shaft 117 furthermore from radially extending in a valve housing 126

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There are passages 127 and 128 for the entry and exit of the medium with a cylindrical seat 129 for the piston. The valve housing 126 belonging to the controller is on the controller housing 118 flanged. The piston 125 stands with the flywheel via various coupling elements 119 in driving connection, thus with a relative movement the centrifugal mass relative to the shaft a longitudinal movement of the piston is brought about. These coupling members consist of a longitudinally displaceable on the shaft 117 mounted ring 130, which carries diametrically opposite two pins 131, each radially through a slot 132 in the shaft 117 in a circumferential groove 133 of the piston 125 engage. The circumferential groove 133 is a closed curve, but which has a slight slope of front, preferably 0.3 mm, so that the pins engaging in the circumferential groove of the rotating together with the shaft Ring to move the piston in an oscillating manner, so that the development of static friction on the piston is prevented. The ring 130 also has an oblique angle on the outer circumference or helical guide groove 134 into which two bolts 135 anchored in flywheel 119 engage radially. When the flywheel 119 leads the shaft 117, i. H. a relative movement occurs between them, the ring 130 thus experiences a longitudinal movement in the axial direction of the controller while the piston 125 is entrained the pins 131 engaging in the circumferential groove of this piston. The brief oscillating movement described above to prevent static friction on the piston, this is done continuously as long as the centrifugal mass and shaft rotate uniformly, on the other hand erfoUgjfc the longitudinal movement of the piston 125, which leads to a Shutting off the oil flow through the passages 127 and 128 in the valve housing only leads to a relative movement the flywheel against the wave, which occurs when the vehicle decelerates.

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With the longitudinal movement of the piston 125, a monitoring length switch 140 can now be actuated by the free End of the piston 125 forms the actuator of this switch, which is adjacent to the valve housing 126 in one is arranged on this flanged housing 141. The monitoring switch 140 is here, for example, an electrical one Switch connected to a display device (not shown), for example in the driver's cab of the vehicle stands.

This is an indication of the operational readiness of the Controller or vice versa, the presence of a fault within the controller is possible, for example a Breakage of the spring between the shaft and the flywheel, which would result in the position of the flywheel opposite the shaft is no longer defined by the longitudinal movement leading to actuation of the monitoring switch of the piston immediately recognizable.

Another preferred weighing device consists of magnets 143, which are installed on one end face of the flywheel 119 and, as they rotate, are located in front of you in the housing 118 of the controller, move the magnetic switch 144 built into it. In this way the rotation of the flywheel becomes a requirement monitored for the functionality of the braking device. For example, if the shaft 117 of an impeller is driven, which rolls on the suspension cable of a cable car, and the impeller would be icy and could no longer rotate, the magnetic switch 144 would indicate that the deceleration controller is incapable is to exercise its function within the braking device.

Due to the size of the spring preload of the spiral spring a certain nominal delay can be achieved. For the Changing the spring preload is one end of the fastening

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the spiral spring can change its position in relation to others. For this reason, the shaft 117 generally has a region of the disk 123 in which the spring end is fixed Notched breathing, which ie interacting with a corresponding Serration on the disc 123 allows the spring end to be set in different positions.

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Claims (1)

1 ι J P a t e β t a ix s ώ r ü e Ii e \ I «, prsmseiiarislitiaBg sum braking relative to each other Seils ρ ait eiiiea feel of lifted brake by a medium pressurized and uwi for braking dracketitlasteten cylinder ^ dadiiroli marked _v that sum derogation regul 'ben BreEssera the cylinder- (7) over a swing-back valve (10) ait eiaeia pressure accumulator (9) for taking up part of the cylinder SirweiGiiencleQ Hediuias <, and also connected via a throttle point (12) with a Ysrzlagungsregulator (13 _S 113} ₉ d © r isit θϊβθε relative movement sensor C14j 16j, 17j 117) so MituahBeverbverbindungs st aasse (19c, 119) uiad @ 1b eieis Voreilea the flywheel- gg over the Rglati ^ Bewegungsuugsamfaefeer up to siaen ? So ₉ 125 <= 129) for that the Esglsr urater susehiDsnder Druckreduzieruiag until reaching the predestiEnatea YerzögeruQgsuertes flowing through Medina on v / e, whereby after, äem by dis Seawuagnaasse caused closing of the Ab = sperrorgaaes the Bruek des Mediuass remains constant for the further braking. 2 _e Breiaseinrichtuiig according to claim 1, characterized in that the relative movement sensor of the deceleration controller (13 $ 113) has a shaft (17, 117) rotating coaxially into a cylindrical shaft corresponding to the relative speed of the parts moving relative to one another Housing (18, 118) is rotatably mounted at both ends, and on which the rotating within the housing (19, 119) is mounted, which is connected to the shaft by means of a driver (20, 120) arranged between the shaft and the flywheel and contrary to the action of between wave and 109848 / 1M0 Flywheel effective force member in the form of a spiral spring (21, 121) can be moved relative to the shaft by a limited angle of rotation. 3. Braking device according to claim 1 and 2, characterized in that that the shut-off element cooperating with the flywheel is a rotary valve (17, 26) which consists of a the shaft (17) rotatable, annular and with the flywheel (19) coupled valve body (26) with radial bores (27) and one having a coaxial (24) and several radial bores (25) connected to it Shaft section (17) consists whose radial ■ bores for the passage of the medium when the Ab- ™ shut-off device with the radial bores in the annular valve body align which valve body (26) when advancing the Sehwung mass (19) opposite the shaft (17) against the force the spiral spring (21) closes the bores (25) in the shaft. and that the housing (18) is connected to a line Outlet opening (30) for the medium to exit the delay controller (13) when the shut-off device is open. 4. Braking device according to claim 1 and 2, characterized in that that that interacts with the flywheel (119) The shut-off element for the medium flowing through the regulator is a piston valve (125-129), which consists of a valve shown in Jj a coaxial bore (124) in the shaft (117) axially movably mounted piston (125) and in one to the controller belonging valve housing (126) radially extending passages (127; 128) for the entry and exit of the medium with a cylindrical seat (129) for the piston, and that the piston with the flywheel via coupling members (130-135) is in driving connection, which coupling members consist of a longitudinally displaceable on the shaft (117) In (130) with at least one pin (131) engaging radially in a circumferential groove (133) of the piston and ait 109848/1740 The outer rim of the ring is helically arranged a guide groove (134) and also made of at least a flywheel attached! and radially into the guide BUi; engaging Bolseii (135) "Order ;, no rotational movement of the flywheel home advancing the same relative to the shaft, - against the force of the effective between the shaft and flywheel mass Sprialfeder - in a aziale movement of the valve piston to be transmitted for the purpose of SeüLiessrasg of para pe rr organs. 5. Braking device according to claim 4? thereby keianse leime t _p öass the Yentilkolbea (125) of the shut-off element sits at its free end the actuating element of a Ueberwachungssohslters (140) which monitors the position of the valve piston vmd. Already connected to a display device 6o BreEäseiiarichtimg according to claim 4 ₅ characterized in that the Us £ s.Bgsm.it (133) ιξ piston of the Eolbenschieber as gssohlosssne Kutyb sit a slope of preferably® 0 _? 3 ms auegebilö © "& ₉ so that the pin eiagreifende least else in üisfangsnut di © of the shaft together with the circumferential Hitiges & Kolhen en ossiliierend" moves sweoks VerhißdariiBg a static friction ,, 7o BreHjseinrichtung according to one or more of the • preceding claims, characterized in that the spiral spring (21, 121) with one end aa of the flywheel (19-119) and attached to the other end aa of the wall (17, 117) and is pretensioned when the shut-off element is open, and that the size of the spring preload is that when the pressure reduction is complete The delay value reached in the medium is determined. 8. Braking device naoh one or more of the preceding claims, characterized in that the pressure accumulator (S) connected to the cylinder (7) is a sub 109848/1740 Contains gas under pressure, rad that the size of the gas bias determines the size of the initial force. 9, braking device according to one or more of the preceding Claims, characterized in that the cylinder is a gel conveyed by a pump (1) for ventilation the brake pressurizes one and, when the pressure is released, the Pulp-actuating spring-loaded cylinder (7) is its outlet by means of an Isei ventilated brake as well is closed by the OeI pressure-loaded brake valve (6), which with a standing under the same oil pressure and exhaust valve (8) that can be actuated for the purpose of braking, and is relieved of pressure after actuation. ™ 10, braking device according to one or more of the above Addresses, characterized in that in a vehicle forming the relative to another moving part the relative movement sensor of the deceleration controller (1 ?, 113) contains an impeller (14) of the vehicle moving relative to a track, which impeller via a gear (16) the rotating shaft (17, 117) of the deceleration regulator (13, 113) drives. 11, braking device according to one or more of the preceding Claims, characterized in that the parts moved relative to one another are a vehicle and for driving the same are certain rails (15), and that the vehicle has four for pressing the braking means against the rails certain spring-loaded cylinders (7) and four associated with these and containing pressurized gas storage (9) and also a delay controller (13, 113) Has trigger valve (8) and a pump (1). 109848/1740